JP7170447B2 - damper device - Google Patents

Description

The present invention relates to damper devices.

A flywheel is attached to the crankshaft of the engine in order to absorb vibrations caused by combustion fluctuations in the engine. Furthermore, a clutch device is provided on the axial transmission side of the flywheel. The clutch device has a clutch disc assembly and a clutch cover assembly.

The clutch disk assembly has a damper device for absorbing and damping torsional vibrations. The clutch cover assembly presses the frictional connection of the clutch disc assembly against the flywheel.

On the other hand, as disclosed in Patent Document 1, a structure in which a damper device is provided in a flywheel assembly is also known. The flywheel assembly of Patent Document 1 has a first flywheel and a second flywheel. The first flywheel is fixed to the crankshaft of the engine. The second flywheel is rotatably supported by the first flywheel, and is elastically connected to the first flywheel in the rotational direction via a damper device.

JP 2007-247723 A

Generally, a damper device is provided with a hysteresis torque generating mechanism. The hysteresis torque generating mechanism of Patent Document 1 is arranged axially side by side with a bearing that supports the second flywheel with respect to the first flywheel.

In the hysteresis torque generating mechanism of Patent Document 1, a large friction area cannot be ensured, and wear of members constituting the hysteresis torque generating mechanism tends to progress. If the wear of the members increases, the desired hysteresis torque cannot be obtained, and the performance of damping vibrations due to rotational fluctuations deteriorates.

SUMMARY OF THE INVENTION It is an object of the present invention to suppress wear of members constituting a hysteresis torque generating mechanism and suppress deterioration of vibration damping performance in a damper device mounted on a device such as a flywheel assembly.

(1) A damper device according to the present invention includes a first rotating member, a second rotating member, a bearing, a damper section, and a first hysteresis torque generating mechanism. The second rotating member is arranged to be rotatable relative to the first rotating member. The bearing rotatably supports the second rotating member with respect to the first rotating member. The damper section has a plurality of elastic members that elastically connect the first rotating member and the second rotating member in the rotational direction. The first hysteresis torque generating mechanism is arranged radially outward of the bearing and generates a first hysteresis torque during relative rotation between the first rotating member and the second rotating member.

In this device, for example, power input to the first rotating member is transmitted to the second rotating member via the damper section. During this power transmission, the first hysteresis torque is generated by the first hysteresis torque generating mechanism, thereby attenuating the vibration caused by the rotation fluctuation.

Here, since the first hysteresis torque generating mechanism is arranged radially outward of the bearing, it is possible to reduce the frictional force required to obtain the desired hysteresis torque. Furthermore, it is possible to increase the diameter of the friction member or the like that constitutes the first hysteresis torque generating mechanism. Therefore, a large friction area can be secured, and the surface pressure for obtaining the necessary frictional force can be reduced. Therefore, it is possible to suppress the wear of the friction member and the like as compared with the conventional device.

(2) Preferably, the bearing is arranged radially inward of the plurality of elastic members. In this case, a particularly large amount of inertia of the second rotating member can be ensured, making it easier to improve the vibration damping performance.

(3) Preferably, the first hysteresis torque generating mechanism has an annular friction member and a biasing member. The friction member has a friction surface. The biasing member presses the friction surface of the friction member against one of the first rotating member and the second rotating member.

Here, the biasing member presses the friction surface of the friction member against one of the first rotating member and the second rotating member. As a result, the first hysteresis torque is generated when the first rotating member and the second rotating member rotate relative to each other.

(4) Preferably, one of the first rotating member and the second rotating member has a pressed surface against which the friction surface of the friction member is pressed. The friction surface and the pressed surface are curved.

Here, by bending the friction surface, the friction area can be increased even with the same diameter. Therefore, wear of the friction member can be further suppressed.

(5) Preferably, the first rotating member has a disc-shaped first plate and a disc-shaped second plate. The second plate is arranged on the first side in the axial direction of the first plate where the second rotating member is arranged, and the outer peripheral portion is fixed to the outer peripheral portion of the first plate. The first hysteresis torque generating mechanism is arranged axially between the second plate and the second rotating member.

Here, it is easy to arrange the members constituting the first hysteresis torque generating mechanism, and it is possible to easily secure a large friction area.

(6) Preferably, the second rotating member has a disk-shaped third plate arranged on the first side in the axial direction of the second plate. The first hysteresis torque generating mechanism is arranged axially between the second plate and the third plate.

Here, since the first hysteresis torque generating mechanism is arranged between the second plate and the third plate, the members constituting the first hysteresis torque generating mechanism can be easily arranged, and a wide friction surface can be easily secured. can.

(7) Preferably, the damper section has a holding plate that holds the elastic member and is connected to the second rotating member , and the holding plate is arranged to face the first rotating member in the axial direction. The first hysteresis torque generating mechanism is arranged between the first rotating member and the holding plate.

(8) Preferably, the first rotating member has a chamber filled with a viscous fluid.

(9) Preferably, the chamber has a sealing portion that blocks entry of fluid from the outside.

(10) Preferably, the vehicle further includes a second hysteresis torque generation mechanism arranged radially inward of the first hysteresis torque generation mechanism and generating the second hysteresis torque within a predetermined angle range.

Here, since the second hysteresis torque is obtained by the second hysteresis torque generating mechanism, it is possible to improve the vibration damping performance of rotational fluctuations.

(11) Preferably, the first hysteresis torque generating mechanism is arranged on the first side in the axial direction of the damper portion, and the second hysteresis torque generating mechanism is arranged on the second side in the axial direction of the damper portion.

(12) Preferably, the elastic member of the damper section has a plurality of outer peripheral side elastic members and a plurality of inner peripheral side elastic members arranged radially inward of the outer peripheral side elastic member. Further, the damper section has an intermediate member that connects the outer peripheral side elastic member and the inner peripheral side elastic member. A third hysteresis torque generating mechanism is provided between the first rotating member and the intermediate member and generates a third hysteresis torque when the first rotating member and the intermediate member rotate relative to each other.

Here, by providing the third hysteresis torque generation mechanism in addition to the first hysteresis torque generation mechanism, wear of the friction member and the like can be further suppressed.

(13) Preferably, an air passage is provided radially inward of the first hysteresis torque generating mechanism and communicates between the chamber and the outside of the chamber.

Here, during operation there can be a negative pressure in the closed chamber. However, since the ventilation path is provided, the inside of the chamber is prevented from becoming negative pressure.

(14) Preferably, the chamber further comprises a one-way valve provided in the vent passage to permit venting from the outside to the inside of the chamber and prohibit reverse.

Here, it is possible to prevent the inside of the chamber from becoming negative pressure, and to prevent the viscous fluid in the chamber from flowing out.

According to the present invention as described above, in a damper device mounted on a device such as a flywheel assembly, it is possible to suppress the wear of the members constituting the hysteresis torque generating mechanism and suppress the deterioration of the vibration damping performance.

1 is a cross-sectional view of a flywheel assembly provided with a damper device according to a first embodiment of the present invention; FIG. FIG. 2 is a partial enlarged view of the upper half of FIG. 1; Partial enlarged view of the lower half of Figure 1 FIG. 2 is a front view of the flywheel assembly of FIG. 1; Sectional drawing of a 1st and 2nd hysteresis torque generating mechanism. The figure corresponding to FIG. 2 of 2nd Embodiment of this invention. The figure corresponding to FIG. 2 of 3rd Embodiment of this invention. The schematic sectional drawing which shows the principal part of 4th Embodiment of this invention. The schematic sectional drawing which shows the seal structure of 5th Embodiment of this invention. The figure which shows the modification of 5th Embodiment. The figure which shows another modification of 5th Embodiment. The figure which shows another modification of 5th Embodiment. The figure which shows the modification of a friction member.

-First Embodiment-
[overall structure]
FIG. 1 is a cross-sectional view of a flywheel assembly provided with a damper device according to a first embodiment of the invention. OO in FIG. 1 is the rotational axis of the flywheel assembly, an engine (not shown) is arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side.

The flywheel assembly 1 is a device for transmitting torque from a crankshaft 10 on the engine side to an input shaft on the transmission side via a clutch device (not shown), and has a function of absorbing and damping torsional vibration due to rotational fluctuations. have. The flywheel assembly 1 mainly includes a first flywheel 2 (an example of a first rotating member), a second flywheel 3 (an example of a second rotating member), a damper section 4, and a first hysteresis torque generating It has a mechanism 5 and a second hysteresis torque generating mechanism 6 .

[First flywheel 2]
The first flywheel 2 can be connected to the crankshaft 10 . As shown in FIG. 2, the first flywheel 2 has a disk-shaped flywheel main body 11 (an example of a first plate) and a disk-shaped plate 12 (an example of a second plate). there is

The flywheel body 11 has an inner cylindrical portion 11a and an outer cylindrical portion 11b.

The inner peripheral cylindrical portion 11a is formed so as to protrude from the inner peripheral end of the flywheel body 11 toward the transmission. The inner cylindrical portion 11a is fixed to the tip of the crankshaft 10 with a bolt 13 (see FIGS. 1 and 3). A bearing 14 is mounted on the outer peripheral surface of the inner peripheral cylindrical portion 11a.

The outer cylindrical portion 11b is formed so as to protrude from the outer peripheral end portion of the flywheel body 11 toward the transmission. A plate 12 is fixed to the tip of the outer cylindrical portion 11b. A ring gear 15 is fixed to the outer peripheral surface of the outer cylindrical portion 11b.

A chamber C is formed inside the first flywheel 2 by the flywheel main body 11 and the plate 12 . The chamber C is filled with a viscous fluid such as grease.

The flywheel main body 11 is formed with a hole 11c for assembly work, and a cover member 17 is attached to the hole 11c. Moreover, the bearing 14 is a sealed bearing provided with a sealing member at the open end. A seal mechanism (not shown) is provided between the first flywheel 2 and the second flywheel 3 . With these, the space in the chamber C is sealed so that the internal viscous fluid does not flow out.

The first hysteresis torque generating mechanism 5 provided between the first flywheel 2 and the second flywheel 3 can also have a sealing function.

[Second flywheel 3]
A clutch device (not shown) is attached to the side surface of the second flywheel 3 . The second flywheel 3 is an annular disk-shaped member and is arranged on the transmission side of the first flywheel 2 so as to face the plate 12 .

A cylindrical portion 3a is formed on the inner peripheral portion of the second flywheel 3 so as to protrude toward the engine. A bearing 14 is provided between the inner peripheral surface of the tubular portion 3 a and the outer peripheral surface of the inner peripheral side tubular portion 11 a of the first flywheel 2 . The second flywheel 3 is supported by the bearing 14 so as to be relatively rotatable with respect to the first flywheel 2 .

[Damper section 4]
The damper part 4 is arranged in the chamber C of the first flywheel 2 and elastically connects the first flywheel 2 and the second flywheel 3 in the rotational direction. As shown in FIGS. 1 to 4, the damper section 4 includes eight outer torsion springs 21 and six inner torsion springs 22, an intermediate member 23, an output flange 24, and first and second stopper mechanisms. 25 and 26. Each torsion spring is hereinafter simply referred to as "spring".

<Outer Spring 21 and Inner Spring 22>
As shown in FIG. 4, the outer springs 21 are arranged side by side in the circumferential direction. Intermediate spring seats 27 are arranged between adjacent outer peripheral springs 21, and the four outer peripheral springs 21 act in series. Two end spring seats 28 are arranged at the ends of the four outer peripheral springs 21 in the circumferential direction. Each of the spring seats 27 and 28 has a tubular portion into which the end of the outer peripheral spring 21 is inserted.

The same applies to the other four outer springs 21 not shown in FIG. That is, the other four outer springs 21 act in series via the intermediate spring seat 27 . Further, end spring seats 28 are arranged at the ends of the other four outer peripheral springs 21 in the circumferential direction.

The six inner springs 22 are arranged radially inward of the outer spring 21 and are arranged side by side in the circumferential direction. The rigidity of the inner peripheral side spring 22 is lower than the rigidity of the outer peripheral side spring 21 .

<Intermediate member 23>
The intermediate member 23 connects the outer spring 21 and the inner spring 22 in series. As shown in FIGS. 2 and 3, the intermediate member 23 has a disk-shaped first side plate 31 and a disk-shaped second side plate 32 facing each other in the axial direction. Each side plate 31, 32 has six holding portions 31a, 32a and two supporting portions 31b, 32b (see FIGS. 3 and 4).

The holding portion 31 a of the first side plate 31 and the holding portion 32 a of the second side plate 32 are arranged to face each other in the axial direction and hold the inner peripheral spring 22 . As a result, the radial and axial movement of the inner peripheral spring 22 is restricted.

The support portions 31b and 32b are formed so as to protrude further radially outward from the outer peripheral portions of the corresponding side plates 31 and 32, respectively. The two support portions 31b and 32b are arranged to face each other with the rotation shaft interposed therebetween.

As shown in FIGS. 3 and 4, a projection 11d is formed on the transmission-side side surface of the flywheel body 11 so as to axially face the support portion 31b of the first side plate 31. As shown in FIGS. A protrusion 12 d is formed on the engine-side side surface of the plate 12 so as to face the support portion 32 b of the second side plate 32 . These protrusions 11d and 12d can come into contact with the end spring seats 28 that support the outer peripheral springs 21 in the rotational direction.

<Output flange 24>
As shown in FIGS. 2 to 4, the output flange 24 is arranged axially between the first and second side plates 31 and 32 that constitute the intermediate member 23 . The output flange 24 is rotatable relative to the intermediate member 23 , and its inner peripheral end portion is fixed to the cylindrical portion 3 a of the second flywheel 3 with rivets 34 . Therefore, the output flange 24 cannot rotate relative to the second flywheel 3 .

The output flange 24 has six windows 24a and internal teeth 24b. The windows 24a are arranged side by side in the circumferential direction and house the inner peripheral springs 22 therein. The internal teeth 24b are formed on the inner peripheral end of the output flange 24 and can mesh with a hub ring 41, which will be described later.

<First and Second Stopper Mechanisms 25, 26>
As described above, the intermediate spring seats 27 and the end spring seats 28 have tubular portions into which the ends of the outer peripheral springs 21 are inserted. As shown in FIG. 4, the radially outer tip surfaces of the adjacent spring seats 27 and 28 can abut against each other. When the flywheel main body 11 and the intermediate member 23 rotate relative to each other by a predetermined angle, the tips of the cylindrical portions of the adjacent spring seats 27 and 28 come into contact with each other. That is, the tip portions of the adjacent spring seats 27 and 28 constitute a second stopper mechanism 26 that limits the operating range of the outer peripheral spring 21 .

Further, as shown in FIG. 4, the outer peripheral surface of the output flange 24 is formed with a notch 24c having a predetermined length in the circumferential direction and opening radially outward. A stopper 36 (see FIGS. 2 and 4) fixed to the intermediate member 23 is accommodated inside the notch 24c. Therefore, when the intermediate member 23 and the output flange 24 rotate relative to each other by a predetermined angle, the stopper 36 comes into contact with the end face of the notch 24c. That is, the notch 24c (the end surface thereof) and the stopper 36 constitute the first stopper mechanism 25, which limits the operating range of the inner peripheral side spring 22. As shown in FIG.

[First Hysteresis Torque Generating Mechanism 5]
The first hysteresis torque generating mechanism 5 is arranged radially outward of the bearing 14 . The first hysteresis torque generating mechanism 5, as shown in FIG. 5, has a first friction member 38 and a first cone spring 39 (an example of a biasing member).

The first friction member 38 is formed in an annular shape, and the side surface on the transmission side serves as a friction surface 38a that contacts the side surface 3b (an example of the surface to be pressed) of the second flywheel 3 . A plurality of engaging projections 38b projecting toward the engine are formed on the outer peripheral portion of the first friction member 38. As shown in FIG. The engaging protrusion 38b is engaged with the engaging hole 12a formed in the plate 12 of the first flywheel 2 without any gap between the outer peripheral surface and the side surface thereof. Therefore, the first friction member 38 cannot rotate relative to the first flywheel 2 and can rotate relative to the second flywheel 3 .

The first cone spring 39 is arranged in a compressed state axially between the plate 12 and the first friction member 38 . Therefore, the first cone spring 39 presses the friction surface 38 a of the first friction member 38 against the pressed surface 3 b of the second flywheel 3 .

With the above configuration, in the first hysteresis torque generating mechanism 5, when the first flywheel 2 and the second flywheel 3 rotate relative to each other, the friction surface 38a and the pressed surface 3b are brought into frictional contact with each other to generate the first hysteresis torque. Occur.

[Second Hysteresis Torque Generating Mechanism 6]
As shown in FIG. 5 , the second hysteresis torque generating mechanism 6 is arranged at substantially the same radial position as the bearing 14 , that is, radially inward of the first hysteresis torque generating mechanism 5 . The second hysteresis torque generating mechanism 6 generates a second hysteresis torque when the first flywheel 2 and the output flange 24 rotate relative to each other beyond a predetermined angle. The second hysteresis torque generating mechanism 6 has a hub ring 41 , a second friction member 42 and a second cone spring 43 .

The hub ring 41 is an annular member and has a plurality of teeth 41a on its outer peripheral surface, as shown in FIG. The hub ring 41 is rotatably mounted on the outer peripheral surface of the inner cylindrical portion 11a of the flywheel main body 11, and the side surface on the transmission side is frictionally engaged with the inner ring of the bearing 14 via a spacer or the like. ing. The teeth 41a of the hub ring 41 mesh with the inner teeth 24b of the output flange 24 with a predetermined gap G (a gap between both sides of the teeth 41a). Therefore, the flywheel body 11 and the hub ring 41 do not rotate relative to each other within the range of the angle θg corresponding to the clearance G between the flywheel body 11 and the output flange 24 . However, when the relative rotation between the flywheel body 11 and the output flange 24 exceeds the angle θg, the hub ring 41 rotates together with the output flange 24 . In this case, the flywheel main body 11 and the hub ring 41 rotate relative to each other.

The second friction member 42 is formed in an annular shape, and the side surface on the transmission side serves as a friction surface 42 a that abuts on the side surface (pressed surface) 41 b of the hub ring 41 . The second cone spring 43 is arranged in a compressed state between the side surface of the flywheel body 11 and the second friction member 42 in the axial direction. Therefore, the second cone spring 43 presses the friction surface 42 a of the second friction member 42 against the pressed surface 41 b of the hub ring 41 .

With the above configuration, when the relative rotation between the flywheel main body 11 and the output flange 24 exceeds the angle θg, the friction surface 42a of the second friction member 42 and the pressed surface 41b of the hub ring 41 come into frictional contact with each other, causing the second hysteresis. A torque generating mechanism 6 generates a second hysteresis torque.

[motion]
<Transmission of torque>
Torque from the crankshaft 10 of the engine is input to the flywheel body 11 of the first flywheel 2 and transmitted to the second flywheel 3 via the damper section 4 .

Specifically, in the damper portion 4 , the inner spring 22 is compressed more than the outer spring 21 because the inner spring 22 has lower rigidity than the outer spring 21 .

When the torsion angle (relative rotation angle) between the intermediate member 23 and the output flange 24 reaches a predetermined value, the first stopper mechanism 25 operates and the compression of the inner peripheral spring 22 stops. Further, when the twist angle between the first flywheel 2 and the intermediate member 23 reaches a predetermined value, the second stopper mechanism 26 operates and the compression of the outer peripheral spring 21 stops.

In this way, the input torque is transmitted through the outer peripheral spring 21, the intermediate member 23, the inner peripheral spring 22, the output flange 24, and the second flywheel 3 to the clutch disk assembly (not shown) and the input torque of the transmission. output to the shaft.

<Operation of first hysteresis torque generating mechanism 5>
When the damper portion 4 is activated, that is, when at least one of the inner spring 22 and the outer spring 21 is compressed, the plate 12 of the first flywheel 2 and the second flywheel 3 rotate relative to each other. Therefore, the first hysteresis torque generating mechanism 5 operates to generate the first hysteresis torque.

Here, since the first hysteresis torque generating mechanism 5 is arranged radially outward of the bearing 14, the diameter of the first friction member 38 can be increased. Therefore, the required frictional force is reduced, and the axial load can be reduced. Furthermore, the friction area increases, and the surface pressure for obtaining the required hysteresis torque can be reduced. Therefore, wear of the first friction member 38 can be suppressed.

<Operation of Second Hysteresis Torque Generating Mechanism 6>
When the transmission torque or torque fluctuation is small and the torsion angle (relative rotation angle) between the first flywheel 2 (that is, the flywheel body 11) and the output flange 24 is θg or less, the hub ring 41 rotates together with the flywheel body 11. The second hysteresis torque generating mechanism 6 does not operate.

On the other hand, when the torsion angle between the flywheel body 11 and the output flange 24 exceeds θg, the teeth 41 a of the hub ring 41 mesh with the inner teeth 24 b of the output flange 24 , and the hub ring 41 rotates together with the output flange 24 . In this state, the second friction member 42 and the hub ring 41 rotate relative to each other. Therefore, the second hysteresis torque generating mechanism 6 operates to generate the second hysteresis torque.

The second hysteresis torque generating mechanism 6 is arranged in the inner peripheral portion of the device as in the conventional device. Therefore, it is difficult to secure a large friction area. However, by increasing the gap between the inner tooth 24b of the output flange 24 and the tooth 41a of the hub ring 41, the operating period can be shortened and wear can be suppressed. Moreover, since the torsional vibration can be damped by the first hysteresis torque generating mechanism 5, even if the second hysteresis torque of the second hysteresis torque generating mechanism 6 is reduced, deterioration of the vibration damping performance can be suppressed. Therefore, the surface pressure of the second friction member 42 of the second hysteresis torque generating mechanism 6 can be reduced, and wear of the second friction member 42 can be suppressed.

Here, the first hysteresis torque generating mechanism 5 is arranged on the transmission side of the damper portion 4 , and the second hysteresis torque generating mechanism 6 is arranged on the engine side of the damper portion 4 . The hysteresis torque generating mechanisms 5 and 6 are provided with cone springs 39 and 43 as biasing members. Therefore, it is possible to suppress the axial vibration of the members constituting the hysteresis torque generating mechanisms 5 and 6, and the hysteresis torque generating mechanisms 5 and 6 can obtain stable hysteresis torque.

-Second Embodiment-
FIG. 6 shows a second embodiment of the invention. The second embodiment has a third hysteresis torque generating mechanism 45 in addition to the configuration of the first embodiment.

The third hysteresis torque generating mechanism 45 is arranged axially between the flywheel main body 11 of the first flywheel 2 and the inner peripheral end of the first side plate 31 of the intermediate member 23 . The third hysteresis torque generating mechanism 45 is arranged radially outward of the bearing 14 and further radially outward than the second hysteresis torque generating mechanism 6 .

The third hysteresis torque generating mechanism 45 has a third friction member 47 and a third cone spring 48 . The third friction member 47 is formed in an annular shape and is in contact with the transmission-side side surface of the flywheel body 11 . The third cone spring 48 is arranged in the axial direction between the third friction member 47 and the first side plate 31 and presses the third friction member 47 against the side surface of the flywheel body 11 .

By providing the third hysteresis torque generating mechanism 45, the vibration damping performance can be further improved. Further, since the third friction member 47 is arranged relatively radially outward, a large friction area can be ensured, and wear can be further suppressed.

-Third Embodiment-
FIG. 7 shows a third embodiment of the invention. A damper device 50 of the third embodiment includes a first flywheel 51, a second flywheel 52, a bearing 53, a damper portion 54, a first hysteresis torque generation mechanism 55, and a second hysteresis torque generation mechanism 56. ,have.

The first flywheel 51 has basically the same configuration as that of the first embodiment, and has a first flywheel body 58 and a plate 59 . Compared to the first embodiment, only the shape of the plate 59 differs, and the plate 59 extends radially inwardly from the plate 12 of the first embodiment.

The second flywheel 52 has a disk-shaped second flywheel main body 61 and a tubular member 62 . The cylindrical member 62 is fixed to the inner peripheral end of the second flywheel body 61 with bolts 63 .

The bearing 53 is mounted on the outer circumferential surface of the inner cylindrical portion 58 a of the first flywheel body 58 and supports the cylindrical member 62 of the second flywheel 52 . That is, the second flywheel 52 is rotatably supported by the first flywheel 51 through the bearings 53 .

The damper portion 54 has an outer peripheral spring 21 , an inner peripheral spring 22 , a connecting member 65 connecting these springs 21 and 22 , and a float member 66 . The outer spring 21 and the inner spring 22 have the same configuration as in the first embodiment.

The connecting member 65 has a first side plate 68 and a second side plate 69 which are axially spaced apart and fixed to each other. The first side plate 68 and the second side plate 69 have holding portions for holding the inner peripheral springs 22, like the side plates 31 and 32 of the first embodiment.

The second side plate 69 has a support portion 69a formed by bending an inner peripheral end toward the engine. Internal teeth similar to the internal teeth 24b of the output flange 24 of the first embodiment are formed on the inner peripheral surface of the support portion 69a. Further, the tip of the tubular member 62 of the second flywheel 52 is welded to the side surface of the support portion 69a on the transmission side.

As described above, the connecting member 65 is fixed to the second flywheel 52 and functions as a member on the output side of the outer peripheral spring 21 and the inner peripheral spring 22 . That is, the connecting member 65 is an example of a second rotating member that can rotate relative to the first flywheel 51 together with the second flywheel 52 .

The float member 66 is rotatable relative to the first side plate 68 and the second side plate 69 and has the function of holding the inner peripheral spring 22 . The inner peripheral end surface of the float member 66 is supported by the outer peripheral surface of the support portion 69a of the second side plate 69 and positioned in the radial direction.

The first hysteresis torque generating mechanism 55 is arranged radially outward of the bearing 53 . The first hysteresis torque generating mechanism 55 has a first friction member 71 and a first cone spring 72 (an example of a biasing member).

The first friction member 71 is formed in an annular shape, and the side surface on the engine side serves as a friction surface 71 a that contacts the side surface of the second side plate 69 . A plurality of engagement projections 71b projecting toward the transmission are formed on the outer peripheral portion of the first friction member 71 . The engaging protrusion 71b is engaged with the engaging hole 59a formed in the plate 59 of the first flywheel 51 without any gap between the outer peripheral surface and the side surface thereof. Therefore, the first friction member 71 cannot rotate relative to the first flywheel 51 and can rotate relative to the second side plate 69 .

The first cone spring 72 is arranged in a compressed state between the plate 59 and the first friction member 71 in the axial direction. Therefore, the first cone spring 72 presses the friction surface 71 a of the first friction member 71 against the side surface of the second side plate 69 .

With the above configuration, the first hysteresis torque generating mechanism 55 generates the first hysteresis torque when the first flywheel 51 and the second side plate 69 (that is, the second flywheel 52 ) rotate relative to each other.

Here, the friction surface 71a of the first friction member 71 is pressed against the side surface of the second side plate 69 by the first cone spring 72, and the engagement projection 71b engages the engagement hole 59a without gaps except for the inner peripheral surface. are in agreement. Therefore, the first hysteresis torque generating mechanism 55 also has a sealing function to prevent external fluid or the like from entering the chamber C through this portion.

Other configurations including the second hysteresis torque generating mechanism 56 are the same as those of the first embodiment.

In the third embodiment, when the damper portion 54 operates and at least one of the outer peripheral spring 21 and the inner peripheral spring 22 expands and contracts, the first hysteresis torque generating mechanism 55 operates to generate the first hysteresis torque. occurs. As in the first embodiment, since the first hysteresis torque generating mechanism 55 is arranged radially outward of the bearing 53, the diameter of the first friction member 71 can be increased. Therefore, the friction area is increased, and the surface pressure for obtaining the required hysteresis torque can be reduced. Therefore, wear of the first friction member 71 can be suppressed.

-Fourth Embodiment-
FIG. 8 shows a fourth embodiment of the invention. In addition to the configuration of the first embodiment, the fourth embodiment further includes an air passage 75 and a one-way valve 76 .

The air passage 75 is provided in a radially extending shape in the inner peripheral cylindrical portion 11a of the flywheel main body 11, which is radially inward of the first hysteresis torque generating mechanism 5 and the second hysteresis torque generating mechanism 6. there is The air passage 75 communicates the chamber C with the outside of the chamber C. As shown in FIG. A one-way valve 76 is provided in the vent passage 75 to allow venting from the outside of the chamber C to the inside of the chamber C and prohibit the reverse.

During the operation of this device, the temperature inside the chamber may exceed 100°C due to the effect of frictional heat. Although the chamber C is basically sealed, there is a minute leak of the internal gas, so if the apparatus is rapidly cooled, the inside of the chamber C becomes negative pressure. If the negative pressure becomes large, there is a risk that the operation of the outer peripheral spring 21 will be impaired. Further, when the negative pressure increases, outside air may pass through each seal portion and foreign matter may enter the chamber. Therefore, by providing the air passage 75 and the one-way valve 76, the viscous fluid is prevented from flowing out from the chamber C and the inside of the chamber C is prevented from becoming negative pressure.

The air passage 75 can be provided in a member different from the inner cylindrical portion 11a, but by providing it in the inner cylindrical portion 11a, the air passage 75 is less likely to be submerged in water, especially when crossing a river. As a result, the risk of water entering the interior of the chamber C can be reduced. The air passage 75 can be configured in a shape different from the shape extending in the radial direction. becomes difficult. In addition, the air passage 75 can also be configured in a shape that bends from the radial direction to the axial direction at the inner peripheral cylindrical portion 11 a of the flywheel main body 11 . Moreover, it is preferable to provide a filter in the middle of the ventilation path 75 or the like.

- Fifth Embodiment -
FIG. 9 shows a fifth embodiment of the invention. In this embodiment, a seal structure 89 is provided.

Specifically, the first hysteresis torque generating mechanism 83 in FIG. 9 is arranged between the plate 12 of the first flywheel 2 and the second flywheel 80 in the axial direction. The first hysteresis torque generating mechanism 83 has a first friction member 84 and a first cone spring 85 .

The first friction member 84 is an annular member and has a friction surface 84a and an engaging projection 84b. The friction surface 84 a contacts the side surface of the second flywheel 80 . The engagement protrusion 84b is engaged with the engagement hole 12a formed in the plate 12. As shown in FIG. Therefore, the first friction member 84 cannot rotate relative to the plate 12 and can rotate relative to the second flywheel 80 .

The first cone spring 85 is arranged axially between the plate 12 and the second flywheel 80 and presses the friction surface 84 a of the first friction member 84 against the side surface of the second flywheel 80 . The outer peripheral end of the first cone spring 85 is fixed to the plate 12 and the inner peripheral end biases the first friction member 84 .

The seal structure 89 also includes an auxiliary member 81 and a sealing cone spring 87 . The auxiliary member 81 is attached to the engine-side side surface of the second flywheel 80 , and is arranged so that the outer peripheral portion faces the inner peripheral end portion of the plate 12 in the axial direction. A sealing cone spring 87 is arranged between the auxiliary member 81 and the plate 12 in the axial direction. The sealing cone spring 87 has a fixed end portion 87a fixed to the plate 12, a press contact end portion 87b pressed against the auxiliary member 81, a surface 87c communicating with the chamber C, and a surface 87d communicating with the outside. , is equipped with The sealing cone spring 87 is configured to press against the auxiliary member 81 with a surface 87c on the side communicating with the chamber C. As shown in FIG.

Therefore, when the pressure in the chamber C becomes negative, an air pressure difference acts on the surface 87d communicating with the outside, and the pressure contact of the surface 87c communicating with the chamber C is strengthened. Therefore, in the seal structure 89, even if a large negative pressure is generated in the chamber C, as indicated by the dashed line, fluid from the outside enters the chamber C by means of the sealing cone spring 87 and the auxiliary member 81. is prevented.

Modifications of the seal structure shown in FIG. 9 are shown in FIGS. 10, 11 and 12. FIG.

In the seal structure shown in FIG. 10, the sealing cone spring 92 is arranged not between the auxiliary member 81 and the plate 12 but between the plate 12 and the second flywheel 80 in the axial direction. The fixed end portion 92 a is fixed to the plate 12 and the press contact end portion 92 b is press contact to the second flywheel 80 .

11, the sealing cone spring 94 is arranged axially between the plate 12 and the second flywheel 80, as in FIG. The fixed end portion 94 a is fixed to the second flywheel 80 and the press contact end portion 94 b is press contact to the plate 12 .

12, the sealing cone spring 96 is arranged between the auxiliary member 81 and the plate 12 in the axial direction, as in FIG. The fixed end portion 96 a is fixed to the auxiliary member 81 , and the press-contact end portion 96 b is press-contacted to the plate 12 .

In any of the above modifications, by pressing the surfaces 92c, 94c, 96c on the side leading to the chamber C against corresponding members, it is possible to prevent external fluids and the like from entering the chamber C. FIG. The seal structure described above can be applied to any of the first to fourth embodiments.

[Other embodiments]
The present invention is not limited to the embodiments as described above, and various modifications or modifications are possible without departing from the scope of the present invention.

(a) In the above embodiment, the friction member is formed of an annular flat plate, but as shown in FIG. 13 , the friction member 90 may be bent. In this case, the mating member with which the friction member 90 abuts must also have the same shape.

In the friction member 90 of this example, a large friction area can be ensured compared to a friction member having the same diameter. Further, since the biasing force P0 of the cone spring (not shown) is the resultant force of the normal force P1 for generating the hysteresis torque and the force P2 along the friction surface, the normal force P1 is greater than the biasing force P0. becomes smaller. Therefore, when the same cone spring is used, the use of a curved friction member reduces the surface pressure compared to a flat plate-like friction member, thereby suppressing wear.

(b) The configuration of the damper section is not limited to the above embodiment. For example, various modifications are possible with respect to the number and arrangement of springs.

1 flywheel assembly 50 damper device 2, 51 first flywheel (first rotating member)
3, 52 second flywheel (second rotating member)
11, 58 flywheel body (first plate)
12, 59 plate (second plate)
14, 53 bearings 4, 54 damper portions 5, 55, 83 first hysteresis torque generating mechanisms 6, 56 second hysteresis torque generating mechanisms 21 outer spring (elastic member)
22 inner peripheral spring (elastic member)
23 intermediate member 65 connecting member 31, 32, 68, 69 side plate (holding plate)
38, 71, 84 First friction member 90 Friction members 39, 85 First cone spring 42 Second friction member 43 Second cone spring 45 Third hysteresis torque generating mechanism 75 Air passage 76 One-way valves 87, 92, 94, 96 Cone spring for sealing

Claims (9)

a first rotating member; and a second rotating member disposed rotatably relative to the first rotating member;
a bearing that rotatably supports the second rotating member with respect to the first rotating member;
a damper section having a plurality of elastic members for transmitting torque from the first rotating member to the second rotating member;
a first hysteresis torque generating mechanism disposed radially outward of the bearing and generating a first hysteresis torque during relative rotation between the first rotating member and the second rotating member;
with
The first rotating member has a disk-shaped first plate and a second plate, respectively, and the second plate is arranged on the first side in the axial direction of the first plate on which the second rotating member is arranged. arranged, the outer peripheral portion is fixed to the outer peripheral portion of the first plate,
The first hysteresis torque generating mechanism is arranged axially between the second plate and the second rotating member,
damper device.
a first rotating member having a chamber filled with a viscous fluid; and a second rotating member disposed rotatably relative to the first rotating member;
a bearing that rotatably supports the second rotating member with respect to the first rotating member;
a damper section having a plurality of elastic members for transmitting torque from the first rotating member to the second rotating member;
A first hysteresis torque that is arranged on the first side in the axial direction of the damper portion and radially outward of the bearing, and that generates a first hysteresis torque when the first rotating member and the second rotating member rotate relative to each other. generation mechanism;
a second hysteresis torque generating mechanism arranged radially inward of the first hysteresis torque generating mechanism on the second side in the axial direction of the damper portion and generating a second hysteresis torque within a predetermined angular range;
a sealing portion that blocks entry of fluid into the chamber from the outside;
A damper device with
3. The damper device according to claim 1, wherein said bearing is arranged radially inward of said plurality of elastic members.
The first hysteresis torque generating mechanism is
an annular friction member having a friction surface;
a biasing member for pressing the friction surface of the friction member against one of the first rotating member and the second rotating member;
having
The damper device according to any one of claims 1 to 3.
one of the first rotating member and the second rotating member has a pressed surface against which the friction surface of the friction member is pressed;
The friction surface and the pressed surface are bent,
The damper device according to claim 4.
The second rotating member has a disk-shaped third plate arranged on the first side in the axial direction of the second plate,
The first hysteresis torque generating mechanism is arranged axially between the second plate and the third plate,
The damper device according to claim 1.
The elastic member of the damper section has a plurality of outer peripheral side elastic members and a plurality of inner peripheral side elastic members arranged radially inward of the outer peripheral side elastic member,
the damper section has an intermediate member that connects the outer peripheral side elastic member and the inner peripheral side elastic member,
A third hysteresis torque generating mechanism disposed between the first rotating member and the intermediate member for generating a third hysteresis torque during relative rotation between the first rotating member and the intermediate member,
A damper device according to any one of claims 1 to 6 .
An air passage provided radially inward of the first hysteresis torque generating mechanism and communicating between the chamber and the outside of the chamber,
The damper device according to claim 2.
9. The damper device according to claim 8 , further comprising a one-way valve provided in said vent passage to permit venting from outside to inside said chamber and prohibit reverse.

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